JPS59191447A - Bearing bracket - Google Patents
Bearing bracketInfo
- Publication number
- JPS59191447A JPS59191447A JP6293083A JP6293083A JPS59191447A JP S59191447 A JPS59191447 A JP S59191447A JP 6293083 A JP6293083 A JP 6293083A JP 6293083 A JP6293083 A JP 6293083A JP S59191447 A JPS59191447 A JP S59191447A
- Authority
- JP
- Japan
- Prior art keywords
- disc
- bearing bracket
- plate thickness
- disk
- reinforcing rib
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
Landscapes
- Engineering & Computer Science (AREA)
- Power Engineering (AREA)
- Motor Or Generator Frames (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の技術分野〕
本発明は立型回転篭機等の回転機に用いられるベアリン
グブラケットに関する。DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a bearing bracket used in a rotating machine such as a vertical rotary cage machine.
従来の立型回転電機のベアリングブラケット構造を電動
機を例にとって第1図に示す。ベアリングブラケットは
内周側のスラスト荷重受圧部(1)に作用する鉛直方向
荷重を円板(2)を介してボルト(3)で結合された外
周板(4)に伝達する機能を有している。ここに電動機
の回転子はスラスト荷重受圧部(1)にのっているため
に、ベアリングブラケットの内外周面の変位差がそのま
ま回転子と固定子の相対変位差となることから置割性構
造が要求される。The bearing bracket structure of a conventional vertical rotating electric machine is shown in FIG. 1, taking an electric motor as an example. The bearing bracket has the function of transmitting the vertical load acting on the thrust load receiving part (1) on the inner circumferential side to the outer circumferential plate (4) connected with the bolt (3) via the disc (2). There is. Here, since the rotor of the electric motor rests on the thrust load receiving part (1), the displacement difference between the inner and outer peripheral surfaces of the bearing bracket directly becomes the relative displacement difference between the rotor and the stator, resulting in a splittable structure. is required.
このためベアリングブラケット円板(2)上に、半径方
向に複数板設置された放射状補強リブ(5) (6)と
円周方向の円周側補強リブ(力(8)及び内径側円周補
強リブ(9)が設けられているのが常である。For this reason, on the bearing bracket disc (2), there are a plurality of radial reinforcing ribs (5) (6) installed in the radial direction and circumferential reinforcing ribs (force (8) and inner radial reinforcing ribs). Ribs (9) are usually provided.
いまベアリングブラケット構造の変形状態について実
変位測定を行えば、変位モードは概略第2図の点線に示
すようになる。すなわち第2図よシ、ベアリングブラケ
ット部の変形は円周方向の円周側補強リブ(7)を境と
して、これよシ内径IIIの変形が大きく、外径側の変
形が小さいことがわかる。このことは半径方向に複数枚
設置せられた放射状補強リブ(5)の剛性が犬であるこ
とによる。したがって、ベアリングブラケット構造の剛
性向上には、第2図に示す円周側補強リブ(力よシ内径
側の剛性をいかに上げるかがポイントとなる。Now, we will examine the deformed state of the bearing bracket structure.
If the displacement is measured, the displacement mode will be approximately as shown by the dotted line in FIG. That is, from FIG. 2, it can be seen that the deformation of the bearing bracket part is larger at the inner diameter III and smaller at the outer diameter side, with the reinforcing rib (7) on the circumferential side as the boundary. This is because the rigidity of the plurality of radial reinforcing ribs (5) installed in the radial direction is moderate. Therefore, in order to improve the rigidity of the bearing bracket structure, the key point is how to increase the rigidity of the inner diameter side of the reinforcing ribs on the circumferential side (as shown in FIG. 2).
従来では、スラスト荷重受圧下の内径側円周補強リブ(
9)の板厚は円板(2)の板厚の0.4〜0.5程度に
トラれているのが常であった。Conventionally, the inner diameter side circumferential reinforcing rib (
The plate thickness of plate 9) was usually about 0.4 to 0.5 of the plate thickness of disk (2).
一方近年ポンプ等の効率向上の問題から、ポンプインペ
ラーとケーシング間の間隙をできるだけ小さくしたいこ
とから前述の回転子と固定子との変形量に制限値を設け
ることが行なわれてきている。又スラスト荷重の大容量
化によシ、従来のベアリングブラケット構造では、上下
方向の剛性が不足で、たとえば全体系の固有振動数が低
下すること、父上記の変形制限値を満足しないこと等で
、剛性をあげるために、すべての板厚を上げる必要があ
り、このことはベアリングブラケット構造の全体的な重
量増加につながる欠点があった。On the other hand, in recent years, in order to improve the efficiency of pumps and the like, and to minimize the gap between the pump impeller and the casing, a limit value has been set for the amount of deformation of the rotor and stator. In addition, due to the increase in thrust load capacity, the conventional bearing bracket structure lacks vertical rigidity, resulting in a decrease in the natural frequency of the entire system, and failure to satisfy the above deformation limit values. In order to increase the rigidity, it was necessary to increase the thickness of all the plates, which had the disadvantage of increasing the overall weight of the bearing bracket structure.
本発明は、上記欠点を改善するためになされたもので、
内径側内周補強リブの剛性を向上させることによ)軽量
で剛性の尚いベアリングブラケットを提供することを目
的とする。The present invention was made to improve the above drawbacks, and
The purpose of the present invention is to provide a lightweight and rigid bearing bracket (by improving the rigidity of the inner peripheral reinforcing rib on the inner diameter side).
上記の目的を達成するため本発明は、外周部が支持され
内周部でスラスト荷重を支持する円板と、この円板に設
けられた複数の放射状補強リブと、円板の内周部に設け
られた内径側円周補強リブとを有するベアリングブラケ
ットにおいて、内径側円周補強リブの板厚と円板の板厚
よυ犬としたことを特徴とする、
〔発明の実施例〕
以下本発明の一実施例について第8図〜第6図を参照し
て説明する。(田は電動機中心軸であシ、この電動機中
心軸(121のまわりに円板(2)が配置されておシ、
この円板(2)は外周部が外周板(4)によシ支持され
、内周部かスラスト荷重を支持するスジスト荷重受圧部
(1)を形成している。この円板(2)には上面下面に
夫々複数枚の放射状補強リブ(5)+6)が固着され、
さらに上面の放射状補強リプ(5)には円周側補強リブ
(力(8)が固着されている。さらに円板(2)の内周
部下面には内径111!+円周補強リプ(9)が固着さ
れている。いま円板(2)の板厚をtI、内径側円周補
強リブ(9)の板厚を+2とし、これらは同一材料によ
多形成されている。In order to achieve the above object, the present invention includes a disk whose outer circumference is supported and whose inner circumference supports a thrust load, a plurality of radial reinforcing ribs provided on the disk, and an inner circumference of the disk. [Embodiments of the Invention] Hereinafter referred to as the present invention, there is provided a bearing bracket having an inner circumferential reinforcing rib, which is characterized in that the plate thickness of the inner circumferential reinforcing rib and the plate thickness of the disk are equal to each other. An embodiment of the invention will be described with reference to FIGS. 8 to 6. (The field is the central axis of the electric motor, and the disk (2) is arranged around this central axis of the electric motor (121).
This disk (2) has an outer circumferential portion supported by an outer circumferential plate (4), and an inner circumferential portion forming a linear load receiving portion (1) that supports a thrust load. A plurality of radial reinforcing ribs (5) + 6) are fixed to the upper and lower surfaces of the disk (2), respectively.
Further, a circumferential reinforcing rib (force (8)) is fixed to the radial reinforcing lip (5) on the upper surface.Furthermore, on the lower surface of the inner periphery of the disc (2), the inner diameter 111! + circumferential reinforcing rib (9 ) is fixed.Now, the plate thickness of the disk (2) is tI, and the plate thickness of the inner diameter side circumferential reinforcing rib (9) is +2, and these are made of the same material.
次に内径側円周補強リブ(9)の板厚t2と、円板(2
)の板厚1.との板厚比t2/lIを変えた場合の重量
変化の割合及びベアリングブラケットの最大変値の変化
を実験値から求めて、第4図及び第6図に示す。これら
の図より本発明の作用・効果について具体的に説明する
。Next, the plate thickness t2 of the inner diameter side circumferential reinforcing rib (9) and the plate thickness t2 of the circular plate (2
) plate thickness 1. The rate of weight change and the change in the maximum variable value of the bearing bracket when changing the plate thickness ratio t2/lI were determined from experimental values and are shown in FIGS. 4 and 6. The functions and effects of the present invention will be specifically explained with reference to these figures.
円板(2)の板厚をtl−al、内径側円周補強リブ(
9)の板厚との板厚比を+2 / tr = 0−4と
する従来構造のベアリングブラケットを例にと9、本発
明の内径側円周補強リブ(9)の、板厚なtt ””
a t、板厚比t2 /” 1を1としたブラケットと
比較する。重量が第4図から9%程度増加しているのに
対して、変位は第5図から40%程度減少し−Cいるの
がわかろう又円板(2)の板厚をtI ”’ a 2、
内径1則円周補強リブ(9)の板厚との板厚比を+2/
tI =0.4とする従来構造のベアリングブラケッ
トを例にとり、本発明の内径側円周補強リブ(9)の板
厚をtI”’=32、板厚比’ t / tIをJとし
たベアリングブラケットと比較すると、itは第4図か
られずか10q6増加するのに対して、変位は第6図か
ら約30チ減少していることがわかる2゜
以上に述べた実験結果の一例かられかるように、本発明
による円板(2)の板厚t1と内径側円周補強リブ(9
)の板厚t2との板厚比tz/11が1以上であるベア
リングブラケット構造は、わずかな重量の増加により剛
性のアップが可能であろう次にこれらの重量増加に対す
る剛性の変化を整理して第6図に示す。$6図では、重
量が軽く、かつ剛性が高いほど即ち変位が小さいほど第
6図のカーブは上昇してゆく。円板)2)の板厚をtI
”’ a 1とすれば、第6図では板厚比12/1.
が38度でこの値は最大値をとる。同様に、円板(2)
の板厚t。The plate thickness of the disk (2) is tl-al, and the inner diameter side circumferential reinforcing rib (
Taking as an example a bearing bracket with a conventional structure in which the plate thickness ratio with the plate thickness of 9) is +2/tr = 0-4, the plate thickness of the inner diameter side circumferential reinforcing rib (9) of the present invention (9) is taken as an example. ”
a t, plate thickness ratio t2/” 1 is compared with the bracket.While the weight has increased by about 9% from Fig. 4, the displacement has decreased by about 40% from Fig. 5. Also, the thickness of disk (2) is tI ''' a 2,
The thickness ratio of the inner diameter and the circumferential reinforcing rib (9) is +2/
Taking as an example a bearing bracket with a conventional structure where tI = 0.4, the plate thickness of the inner diameter side circumferential reinforcing rib (9) of the present invention is tI"' = 32, and the plate thickness ratio 't/tI is J. Compared to the bracket, it increases by only 10q6 from Figure 4, while the displacement decreases by about 30cm from Figure 6. This can be seen from an example of the experimental results mentioned above. As shown in FIG.
) The bearing bracket structure in which the plate thickness ratio tz/11 with plate thickness t2 is 1 or more will be able to increase the rigidity with a slight increase in weight.Next, we will summarize the changes in rigidity with respect to these weight increases. This is shown in Figure 6. In Figure 6, the lighter the weight and the higher the rigidity, that is, the smaller the displacement, the higher the curve in Figure 6 becomes. The plate thickness of disk) 2) is tI
``' If a is 1, the plate thickness ratio in Fig. 6 is 12/1.
This value takes the maximum value at 38 degrees. Similarly, disk (2)
Plate thickness t.
をa2 + ”3 + ”4としたときの板厚比は、約
3.0゜2.0,1.0程度でこの値は最大値をとるこ
とがわかった。即ちとの車量増加に対する剛性の変化の
比が極大値をとる近傍にt 2 / t 、の比を設定
すれば、重量増加が最小にし最大の効果を得ることが可
能となるものである。ここでa1〜a4の値は、ベアリ
ングブラケット構造として通常用いられると考えられる
2(HR1〜100關の範囲にとっている。It was found that the plate thickness ratio when a2 + "3 + "4 is approximately 3.0°2.0, 1.0, and this value takes the maximum value. That is, by setting the ratio t 2 /t near the maximum value of the ratio of the change in rigidity to the increase in vehicle volume, it is possible to minimize the increase in weight and obtain the maximum effect. Here, the values of a1 to a4 are set in the range of 2 (HR1 to 100), which is considered to be normally used as a bearing bracket structure.
又必ずしも極大値をとらずとも、円板(2)の板厚1、
と内径側円周補強リブ(9)の板厚t2との板厚比1、
/1を1以上とすることによシ軽量でかつ高剛性のベア
リングブラケット構造が可能となる。Also, even if the thickness of disk (2) is 1, even if it does not necessarily take the maximum value,
and the plate thickness t2 of the inner diameter side circumferential reinforcing rib (9), the plate thickness ratio is 1,
By setting /1 to 1 or more, a lightweight and highly rigid bearing bracket structure is possible.
第7図は、本発明の他の実施例を示したものでスラスト
荷重受圧部内径側に複数枚の内径側円周補強リブ(9)
0(2)を備え、かつこれらの板厚の合計と円板(2)
との板厚比を1以上とするものである。この実施例にお
いても前記と同様の効果を奏することができる。FIG. 7 shows another embodiment of the present invention, in which a plurality of inner circumferential reinforcing ribs (9) are provided on the inner diameter side of the thrust load receiving part.
0(2), and the sum of these plate thicknesses and the disk (2)
The plate thickness ratio between the plate and the plate is 1 or more. This embodiment can also produce the same effects as described above.
又本発明では、円板(2)の下に設けられる内径側円周
補強リブ(9)の軸方向の高さについては言及していな
いが、この高さは、高ければ高いほど剛性が増加するこ
とは言うまでもない。しかし軸方向の電動機の長さが増
加することにより、回転子等の長さが増加する等コスト
アップになるために通常100 a〜200順程度に制
限されているのが常である。Further, the present invention does not mention the height in the axial direction of the inner circumferential reinforcing rib (9) provided under the disk (2), but the higher the height, the higher the rigidity. It goes without saying that you should. However, as the length of the electric motor in the axial direction increases, the length of the rotor and the like increases, resulting in an increase in cost, so it is usually limited to about 100 mm to 200 mm.
第8図に、他の実施例を示す。円板(2)の下に設けら
れた複数板の内径側円周補強リブ(9) unの下面に
、蓋aυを備えても良い。FIG. 8 shows another embodiment. A lid aυ may be provided on the lower surface of the inner circumferential reinforcing rib (9) of the plurality of plates provided under the disk (2).
以上説明したように、本発明によれば高剛性でかつ重量
増加を最小とするベアリングブラケットが可能となるも
ので、本発明の実施による効果は犬である。As explained above, according to the present invention, it is possible to provide a bearing bracket that has high rigidity and minimizes weight increase, and the effects of carrying out the present invention are significant.
第1図は従来のベアリングブラケットを示す断面図、第
2図は、従来のベアリングブラケットの変形状態を示す
状態図、第3図は、本発明の一実施例を示す断面図、第
4図は、板厚比12/1.と重量の関係を示す線図、第
5図は板厚比i 2/ i 1と変位の関係を示す線図
、第6図は、板厚比1./1.と車量増加に対する剛性
比の関係を示す線図、第奢図及び第8=図は本発明の他
の実施例を示す断面図である。
1・・・スラスト荷重受圧部、2・・・円板、3・・・
ボルト、4・・・外周板、
5.6・・・放射状補強リブ、7,8・・・円周側補強
リブ、9.10・・・内径側円周補強リブ、11・・・
補強蓋、12・・・電動機中心軸。
代理人 弁理士別 近 憲 佑 (ほか1名)第1図
第2図
第3図
第4図
第5図
t2/ど。
第6図
θ4/ 2 3 4 5
ど 7t2/l/
$7図
第8図Fig. 1 is a sectional view showing a conventional bearing bracket, Fig. 2 is a state diagram showing a deformed state of the conventional bearing bracket, Fig. 3 is a sectional view showing an embodiment of the present invention, and Fig. 4 is a sectional view showing a conventional bearing bracket. , plate thickness ratio 12/1. FIG. 5 is a diagram showing the relationship between plate thickness ratio i 2 / i 1 and displacement. FIG. 6 is a diagram showing the relationship between plate thickness ratio i 2 / i 1 and displacement. /1. A diagram showing the relationship between rigidity ratio and an increase in vehicle volume, Figure 8, and Figure 8 are cross-sectional views showing other embodiments of the present invention. 1... Thrust load receiving part, 2... Disc, 3...
Bolt, 4... Outer peripheral plate, 5.6... Radial reinforcing rib, 7, 8... Circumferential reinforcing rib, 9.10... Inner circumferential reinforcing rib, 11...
Reinforcement lid, 12...Electric motor center shaft. Agent: Kensuke Chika (and 1 other person) by patent attorney Figure 1 Figure 2 Figure 3 Figure 4 Figure 5 t2/d. Fig. 6 θ4/ 2 3 4 5
Do 7t2/l/$7Figure 8
Claims (3)
持する円板と、この円板に設けられた複数の放射状補強
ソッと、円板の内周部に設けられた内径側円周補強リブ
とを有するベアリングブラケットにおいて、内径側円周
補強リブの板厚を円板の板厚よシ犬としたことを特徴と
するベアリングブラケット。(1) A disc whose outer periphery is supported and whose inner periphery supports thrust loads, a plurality of radial reinforcing rods provided on this disc, and inner circumferential reinforcement provided on the inner periphery of the disc. 1. A bearing bracket having a rib, characterized in that the thickness of the inner circumferential reinforcing rib is equal to the thickness of the disk.
比を、剛性/重量の比が最大値をとる近傍に選定したこ
とを特徴とする特許請求の範囲第1項に記載のベアリン
グブラケット。(2) The ratio of the plate thickness of the inner diameter side circumferential reinforcing rib to the plate thickness of the disk is selected to be close to the maximum value of the stiffness/weight ratio. bearing bracket.
けたことを特徴とする特許請求の範囲第1項に記載のベ
アリングブラケット。(3) The bearing bracket according to claim 1, characterized in that a plurality of circumferential reinforcing lips with an inner diameter of 11 are provided in the radial direction.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP6293083A JPS59191447A (en) | 1983-04-12 | 1983-04-12 | Bearing bracket |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP6293083A JPS59191447A (en) | 1983-04-12 | 1983-04-12 | Bearing bracket |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS59191447A true JPS59191447A (en) | 1984-10-30 |
Family
ID=13214486
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP6293083A Pending JPS59191447A (en) | 1983-04-12 | 1983-04-12 | Bearing bracket |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS59191447A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2007205435A (en) * | 2006-01-31 | 2007-08-16 | Hitachi Ltd | Hydraulic shock absorber |
JP2009036256A (en) * | 2007-07-31 | 2009-02-19 | Kayaba Ind Co Ltd | Water system hydraulic buffer |
-
1983
- 1983-04-12 JP JP6293083A patent/JPS59191447A/en active Pending
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2007205435A (en) * | 2006-01-31 | 2007-08-16 | Hitachi Ltd | Hydraulic shock absorber |
JP2009036256A (en) * | 2007-07-31 | 2009-02-19 | Kayaba Ind Co Ltd | Water system hydraulic buffer |
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